DE102015007424A1 - Pressure control device - Google Patents
Pressure control device Download PDFInfo
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- DE102015007424A1 DE102015007424A1 DE102015007424.5A DE102015007424A DE102015007424A1 DE 102015007424 A1 DE102015007424 A1 DE 102015007424A1 DE 102015007424 A DE102015007424 A DE 102015007424A DE 102015007424 A1 DE102015007424 A1 DE 102015007424A1
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- 230000001419 dependent effect Effects 0.000 description 2
- 238000001514 detection method Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 239000000314 lubricant Substances 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000003860 storage Methods 0.000 description 2
- 238000003466 welding Methods 0.000 description 2
- BUHVIAUBTBOHAG-FOYDDCNASA-N (2r,3r,4s,5r)-2-[6-[[2-(3,5-dimethoxyphenyl)-2-(2-methylphenyl)ethyl]amino]purin-9-yl]-5-(hydroxymethyl)oxolane-3,4-diol Chemical compound COC1=CC(OC)=CC(C(CNC=2C=3N=CN(C=3N=CN=2)[C@H]2[C@@H]([C@H](O)[C@@H](CO)O2)O)C=2C(=CC=CC=2)C)=C1 BUHVIAUBTBOHAG-FOYDDCNASA-N 0.000 description 1
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- 230000002349 favourable effect Effects 0.000 description 1
- 230000005669 field effect Effects 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000004088 simulation Methods 0.000 description 1
- 230000002123 temporal effect Effects 0.000 description 1
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- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D16/00—Control of fluid pressure
- G05D16/20—Control of fluid pressure characterised by the use of electric means
- G05D16/2006—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means
- G05D16/2013—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means
- G05D16/2026—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means with a plurality of throttling means
- G05D16/2046—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means with a plurality of throttling means the plurality of throttling means being arranged for the control of a single pressure from a plurality of converging pressures
- G05D16/2053—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means with a plurality of throttling means the plurality of throttling means being arranged for the control of a single pressure from a plurality of converging pressures the plurality of throttling means comprising only a first throttling means acting on a higher pressure and a second throttling means acting on a lower pressure, e.g. the atmosphere
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D16/00—Control of fluid pressure
- G05D16/20—Control of fluid pressure characterised by the use of electric means
- G05D16/2006—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means
- G05D16/2013—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means
- G05D16/202—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means actuated by an electric motor
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D16/00—Control of fluid pressure
- G05D16/20—Control of fluid pressure characterised by the use of electric means
- G05D16/2006—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means
- G05D16/2013—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means
- G05D16/2026—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means with a plurality of throttling means
- G05D16/2033—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means with a plurality of throttling means the plurality of throttling means being arranged in series
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05B—CONTROL OR REGULATING SYSTEMS IN GENERAL; FUNCTIONAL ELEMENTS OF SUCH SYSTEMS; MONITORING OR TESTING ARRANGEMENTS FOR SUCH SYSTEMS OR ELEMENTS
- G05B11/00—Automatic controllers
- G05B11/01—Automatic controllers electric
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05B—CONTROL OR REGULATING SYSTEMS IN GENERAL; FUNCTIONAL ELEMENTS OF SUCH SYSTEMS; MONITORING OR TESTING ARRANGEMENTS FOR SUCH SYSTEMS OR ELEMENTS
- G05B6/00—Internal feedback arrangements for obtaining particular characteristics, e.g. proportional, integral or differential
- G05B6/02—Internal feedback arrangements for obtaining particular characteristics, e.g. proportional, integral or differential electric
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D16/00—Control of fluid pressure
- G05D16/20—Control of fluid pressure characterised by the use of electric means
- G05D16/2006—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means
- G05D16/2013—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means
- G05D16/2026—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means with a plurality of throttling means
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D16/00—Control of fluid pressure
- G05D16/20—Control of fluid pressure characterised by the use of electric means
- G05D16/2006—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means
- G05D16/2013—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means
- G05D16/2026—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means with a plurality of throttling means
- G05D16/2046—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means with a plurality of throttling means the plurality of throttling means being arranged for the control of a single pressure from a plurality of converging pressures
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- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Physics & Mathematics (AREA)
- Engineering & Computer Science (AREA)
- Automation & Control Theory (AREA)
- Control Of Fluid Pressure (AREA)
- Magnetically Actuated Valves (AREA)
Abstract
Druckregelvorrichtung, bestehend aus mindestens – zwei Schaltventilen (10, 12), – einer Regeleinrichtung (14), – einer Sensoreinrichtung (20), und – einer Spannungsversorgung (24).Pressure control device, comprising at least - two switching valves (10, 12), - a control device (14), - a sensor device (20), and - a power supply (24).
Description
Die Erfindung betrifft eine Druckregelvorrichtung zur stetigen Einstellung von Hydrauliksystemen.The invention relates to a pressure control device for the continuous adjustment of hydraulic systems.
Üblicherweise werden zur stetigen Einstellung eines Hydrauliksystems sog. Proportionalventile eingesetzt. Diese Proportionalventile sind Steuergeräte mit elektrischem Eingangssignal, die ein Hydrauliksystem nach Steuerungsanweisung mit stetiger Signalbildung einstellen, um die Ausgangsgröße der Strecke, beispielsweise in Form der Kraft eines hydraulischen Arbeitszylinders, stetig zu beeinflussen.Usually so-called proportional valves are used for the continuous adjustment of a hydraulic system. These proportional valves are electrical input signal controllers that adjust a hydraulic system according to a control signal with continuous signal formation to continuously influence the output of the circuit, for example in the form of the force of a hydraulic working cylinder.
Eingabeglied für das elektrische Signal, insbesondere in Form von Strom, ist der sog. Proportionalmagnet, der ein elektrisches Signal in eine Kraft umwandelt. Der Proportionalmagnet übt über das von ihm erzeugte Magnetfeld eine Kraft auf einen ferromagnetischen Körper aus, regelmäßig in Form eines Magnetankers. Über eine Anpassung der Steuergeometrie in Verbindung mit einer unmagnetischen Zone kann die Magnetkraft-Hub-Kennlinie dahingehend variieren, dass eine nahezu wegunabhängige konstante Magnetkraft erzeugt werden kann. Die unmagnetische Zone wird üblicherweise durch einen Schweißprozess erzeugt, welcher, um eine gleichbleibende Qualität erzielen zu können, mit einem sehr hohen Aufwand überwacht werden muss. Das angesprochene elektrische Signal wird von einer Verstärkerelektronik mit interner Stromregelung erzeugt. Dabei wird die Widerstandsänderung der Spule durch den elektrischen Strom kompensiert sowie die Strombeeinflussung durch die Bewegung des ferromagnetischen Ankers im Magnetfeld. Üblicherweise muss auch ein überlagerter, sog. Dither zur Reibungsminimierung angewendet werden. Diese Maßnahmen zur Reibungsminimierung auf der elektrischen Seite des Ventils erfordern dann wiederum geeignete Maßnahmen beim mechanischen Teil des Proportionalventils, wie die Lagerung des ferromagnetischen Ankers und hochgenau bearbeitete Flächen zur Führung der mechanischen Bauteile.The input element for the electrical signal, in particular in the form of current, is the so-called proportional magnet, which converts an electrical signal into a force. The proportional magnet exerts a force on a ferromagnetic body via the magnetic field generated by it, regularly in the form of a magnet armature. By adjusting the control geometry in conjunction with a non-magnetic zone, the magnetic force-stroke characteristic can vary in such a way that a nearly path-independent constant magnetic force can be generated. The non-magnetic zone is usually produced by a welding process, which in order to achieve a consistent quality, must be monitored with a very high cost. The mentioned electrical signal is generated by an amplifier electronics with internal current control. The resistance change of the coil is compensated by the electric current and the current influence by the movement of the ferromagnetic armature in the magnetic field. Usually, a superimposed, so-called dither must also be used to minimize friction. These measures to minimize friction on the electrical side of the valve then in turn require appropriate measures in the mechanical part of the proportional valve, such as the storage of the ferromagnetic armature and highly accurately machined surfaces for guiding the mechanical components.
Um die vorstehend beschriebenen Nachteile von Proportionalventilen zu vermeiden, ist in der
Das dahingehend bekannte Verfahren wird auf eine hydraulische Steuerung zur Versorgung und zeit- und mengengenauen Dosierung von Schmierstoff an einer Schmierstelle in einem 2-Takt-Großdieselmotor eingesetzt. Die Schmiermenge wird dabei über ein 2/2-Wege-Ventil dosiert, welches ballistisch angesteuert wird. Das heißt, das Ventil wird über Strompulse kurzer Dauer angesteuert, die in der Regel nicht ausreichen, den Ventilkolben in seine Endlage bei voller Öffnung zu bringen. Der Öffnungshub erfolgt ballistisch, d. h. der Kolben wird durch die pulsartige Magnetbetätigung in Öffnungsrichtung gestoßen und fällt unter Einwirkung der entgegengesetzt dieser Bewegung wirkenden Ventilfeder und den am Ventil anstehenden Strömungskräften wieder in seine geschlossene Endlage zurück. Die Dauer des Pulses bestimmt dabei die pro ballistischen Öffnungshub dosierte Ölmenge. Mit dem genannten Betriebsmodus lassen sich bei der bekannten Ansteuerlösung mittlere Volumenströme einstellen, die beispielsweise um einen Faktor 1/10000 unter dem Nennvolumenstrom des Grundventils liegen können.The well-known method is used on a hydraulic control for supply and time and quantity precise metering of lubricant at a lubrication point in a 2-stroke large diesel engine. The amount of lubricant is metered via a 2/2-way valve, which is controlled ballistically. That is, the valve is driven by current pulses short duration, which are usually not sufficient to bring the valve piston in its end position at full opening. The opening stroke is ballistic, d. H. the piston is pushed by the pulse-like magnetic actuation in the opening direction and falls back under the action of the opposite of this movement acting valve spring and the pending flow forces back to its closed end position. The duration of the pulse determines the metered per ballistic opening stroke amount of oil. With the aforementioned operating mode can be set in the known control solution medium volume flows, which may be, for example, by a factor of 1/10000 below the nominal volume flow of the base valve.
Ausgehend von diesem Stand der Technik liegt der Erfindung die Aufgabe zugrunde, handelsübliche Proportional-Druckregelventile von ihrem Ventilverhalten her mit vereinfachten Mitteln und somit kostengünstig sowie in funktionssicherer Weise mit anderen Mitteln zu realisieren.Based on this prior art, the present invention seeks to realize commercial proportional pressure control valves of their valve behavior forth with simplified means and thus cost-effectively and in a functionally reliable manner by other means.
Eine dahingehende Aufgabe löst eine Druckregelvorrichtung mit den Merkmalen des Patentanspruchs 1, bestehend aus mindestens
- – zwei, vorzugsweise sitzdicht ausgebildeten, Schaltventilen,
- – einer Regeleinrichtung,
- – einer Sensoreinrichtung, insbesondere einer Drucksensoreinrichtung, und
- – einer Spannungsversorgung.
- Two, preferably seat-tight, switching valves,
- - a control device,
- - A sensor device, in particular a pressure sensor device, and
- - a power supply.
Mit der erfindungsgemäßen Lösung ist es möglich, besonders einfach die Ausgangsgröße einer Strecke mit Schaltventilen, vorzugsweise mit sitzdichten Schaltventilen, und ohne komplexe Verstärkerelektronik, stetig einzustellen. Die erfindungsgemäße Lösung ermöglicht ein verschleißarmes Schalten des jeweiligen Ventils. Alle etwaig auftretenden Nichtlinearitäten werden durch die Regeleinrichtung derart günstig beeinflusst, dass jedenfalls eine stetige Einstellung ermöglicht ist. Die erfindungsgemäße Druckregelvorrichtung ist dabei besonders effizient im Umgang mit hydraulischer Energie.With the solution according to the invention, it is possible to adjust the output variable of a route with switching valves, preferably with seat-tight switching valves, and without complex amplifier electronics, particularly easily. The solution according to the invention enables low-wear switching of the respective valve. Any nonlinearities that may occur are so favorably influenced by the control device that, in any case, a continuous adjustment is possible. The pressure control device according to the invention is particularly efficient in dealing with hydraulic energy.
Die nach der Erfindung eingesetzten Schaltventile sind vom konstruktiven Aufbau des Magnetsystems her wesentlich einfacher als Proportionalventile zu realisieren. Insbesondere das Steuer-Konussystem kann einfacher realisiert werden, da man nicht zwingend, wie beim Proportional-Druckregelventil, im Wesentlichen horizontal verlaufende Kraft-Hub-Kennlinien einzuhalten braucht. Alle Abweichungen bezüglich der Magnetkraft, welche durch den Schweißprozess und durch die Fertigung bei den bekannten Proportionalventilen entstehen, spielen keine Rolle, solange eine Mindestkraft erreicht wird. Das Gleiche gilt auch für die Varianz der Magnetkraftlinie in der Serienproduktion. Des Weiteren ist eine übliche Lagerung des Magnetankers mit DU-Lager zur Reibungsreduzierung sowie die Dither-Ansteuerung nicht notwendig.The switching valves used according to the invention are much simpler to implement from the structural design of the magnet system as proportional valves. In particular, the control cone system can be realized more easily, since it is not mandatory, as in the proportional pressure control valve, to comply with substantially horizontally extending force-stroke characteristics. All deviations in the magnetic force caused by the welding process and by the production at the occur known proportional valves, play no role as long as a minimum force is achieved. The same applies to the variance of the magnetic force line in series production. Furthermore, a conventional storage of the armature with DU bearings for friction reduction and dither drive is not necessary.
In Kombination mit einer oder mehreren Sensoreinrichtungen, insbesondere unter Einsatz mindestens eines Drucksensors, und einer geeigneten Mikroprozessoreinheit ergibt sich die Möglichkeit, vollwertige Proportionalventile in einfacher Weise nachzubauen. Dabei genügen Prozessoren mit geringer Taktfrequenz, was die Kosten für die Gesamt-Druckregelvorrichtung senken hilft.In combination with one or more sensor devices, in particular with the use of at least one pressure sensor, and a suitable microprocessor unit, it is possible to simulate fully proportional valves in a simple manner. All it takes is processors with a low clock frequency, which helps lower the costs for the overall pressure regulator.
Der im Rahmen der Druckregelvorrichtung eingesetzte Regelkreis besteht aus der Regeleinrichtung selbst, dem Stellglied regelmäßig bestehend aus dem eigentlichen Magnetventil und einem Ventiltreiber, dem Hydrauliksystem und dem bereits angesprochenen Sensor. Dieser Sensor der Sensoreinrichtung sendet den aktuellen Messwert oder Ist-Wert als Signal zum Mikroprozessor. Dieser vergleicht dann diesen Ist-Wert mit dem Soll-Wert, der von einer übergeordneten Eingabestelle zum Mikroprozessor gelangt. In Abhängigkeit der Größe des Fehlers e, der sich aus der Differenz von Soll-Wert mit dem Ist-Wert ergibt, bestimmt der Mikroprozessor die weitere Schaltweise für die eingesetzten beiden Ventile. Durch dieses System wird ein proportionales Verhalten eines Proportional-Druckregelventils mit zwei einfachen Schaltventilen erreicht. Dahingehende Schaltventile haben im Gegensatz zu Proportionalventilen keine Hysterese und mit der erfindungsgemäßen Druckregelvorrichtung lassen sich ohne weiteres eine Druckminderfunktion, eine Druckbegrenzung oder eine Druckregelung realisieren.The control circuit used in the context of the pressure control device consists of the control device itself, the actuator regularly consisting of the actual solenoid valve and a valve driver, the hydraulic system and the already mentioned sensor. This sensor of the sensor device sends the current measured value or actual value as a signal to the microprocessor. This then compares this actual value with the desired value, which passes from a higher-level input location to the microprocessor. Depending on the size of the error e, which results from the difference between the desired value and the actual value, the microprocessor determines the further switching mode for the two valves used. Through this system, a proportional behavior of a proportional pressure control valve is achieved with two simple switching valves. These switching valves have in contrast to proportional valves no hysteresis and with the pressure control device according to the invention can be readily realize a pressure reducing function, a pressure relief or pressure control.
Im Folgenden wird die erfindungsgemäße Druckregelvorrichtung anhand eines Ausführungsbeispiels nach der Zeichnung näher erläutert. Dabei zeigen in prinzipieller und nicht maßstäblicher Darstellung dieIn the following, the pressure control device according to the invention will be explained in more detail using an exemplary embodiment according to the drawing. This show in principle and not to scale representation of the
Zunächst sei anhand eines handelsüblichen Proportional-Druckregelventils kurz dessen Funktion erklärt, die auch mit der erfindungsgemäßen Druckregelvorrichtung realisiert werden soll. Bei den dahingehenden Druckreglern handelt es sich regelmäßig um solche in Schieberbauweise. Im unbestromten Zustand ist dabei der Druckversorgungs- oder Pumpenanschluss verschlossen. Ferner ist der Verbraucheranschluss mit dem Tankanschluss fluidführend verbunden. Wird nun ein Stromsignal an den Proportionalmagneten des Druckregelventils angelegt, drückt der Magnet mit einer der Höhe des Steuerstroms entsprechenden Kraft auf den Regelkolben des Ventils. Dadurch wird der Regelkolben gegen eine Rückstellfeder verschoben und das Hydrauliköl strömt vom Druckversorgungs- oder Pumpenanschluss zum Verbraucheranschluss. Durch einen am Verbraucheranschluss angeschlossenen hydraulischen Verbraucher, beispielsweise in Form eines Wege-Schieberventils, baut sich am Verbraucheranschluss ein Druck auf, der beispielsweise auf einen Druckmeldestift des Proportional-Druckregelventils einwirken kann und insoweit eine Gegenkraft zur Kraft des Proportionalmagneten erzeugt. Dadurch ergibt sich wiederum eine Bewegung des Regelkolbens mit dem Druckmeldestift zurück in die vorstehend beschriebene Ausgangslage, was zur Folge hat, dass der Zufluss vom Druckversorgungs- oder Pumpenanschluss zum Verbraucheranschluss verringert wird, bis wiederum der am Verbraucheranschluss anliegende Druck der Magnetkraft abzüglich der Federkraft der Rückstellfeder und damit der Druckwert-Vorgabe über dem anstehenden Stromsignal entspricht. Benötigt der angeschlossene Verbraucher am Verbraucheranschluss keine Druckflüssigkeit mehr, beispielsweise weil das angesprochene Wege-Schieberventil sich am Anschlag befindet, bewegt sich der Regelkolben weiter zurück und verschließt die Zulaufbohrungen.First, a function of a commercially available proportional pressure control valve briefly explains its function, which is also to be realized with the pressure control device according to the invention. The pertinent pressure regulators are usually those in slide construction. In the de-energized state, the pressure supply or pump connection is closed. Furthermore, the consumer connection is fluid-conducting connected to the tank connection. If a current signal is now applied to the proportional magnet of the pressure regulating valve, the magnet presses with a force corresponding to the magnitude of the control current onto the control piston of the valve. As a result, the control piston is displaced against a return spring and the hydraulic oil flows from the pressure supply or pump port to the load port. A hydraulic consumer connected to the consumer connection, for example in the form of a directional spool valve, builds up a pressure on the consumer connection, which can act, for example, on a pressure-sensing stylus of the proportional pressure-regulating valve and thus generates a counterforce to the force of the proportional magnet. This in turn results in a movement of the control piston with the pressure detection pin back into the starting position described above, which has the consequence that the inflow from the pressure supply or pump connection to the load port is reduced, in turn, applied to the load port pressure of the magnetic force minus the spring force of the return spring and thus corresponds to the pressure value specification above the pending current signal. If the connected consumer no longer requires any pressurized fluid at the consumer connection, for example because the addressed directional spool valve is located at the stop, the regulating piston moves further back and closes the inlet bores.
Fällt der Ausgangsdruck durch die Entlastung des Verbrauchers am Verbraucheranschluss des Ventils unter die Druckvorgabe, drückt der Magnetanker den Regelkolben wiederum in eine Regelposition und der Regelvorgang beginnt erneut. Der maximal erreichbare Regeldruck wird dabei durch die Magnetkraft des Proportionalmagneten dem Grunde nach festgelegt. Steigt der Druck am Verbraucheranschluss über den Vorgabewert an, wird der Regelkolben mit dem Magnetanker derart verschoben, dass die Verbindung vom Verbraucheranschluss zum Tankanschluss geöffnet wird. Hierdurch lässt sich der Druck am Verbraucheranschluss begrenzen. Im Falle einer Unterbrechung des Steuerstroms wird der Regelkolben vom Druck am Verbraucheranschluss und der Rückstellfeder zurückgezogen. Dadurch wird der Verbraucheranschluss mit dem Tankanschluss verbunden und der Verbraucherdruck am Verbraucheranschluss fällt auf das Tankniveau, das am Tankanschluss ansteht, ab.If the output pressure falls below the pressure set by relieving the load at the consumer connection of the valve, the armature again forces the control piston into a control position and the control process starts again. The maximum achievable control pressure is determined by the magnetic force of the proportional magnet in the reason. If the pressure at the consumer connection rises above the specified value, the control piston with the magnet armature is displaced in such a way that the connection from the consumer connection to the tank connection is opened. This limits the pressure at the consumer connection. In case of interruption of the control current, the control piston is withdrawn from the pressure at the load port and the return spring. This connects the load port to the tank port and the consumer pressure at the load port drops to the tank level at the tank port.
Die vorstehend beschriebene bekannte Druckregelfunktion für ein handelsübliches Proportional-Druckregelventil wird nunmehr gemäß der Erfindung mit zwei sitzdichten 2/2-Wege-Schaltventilen nachgebildet. Dabei erlauben die dahingehenden sitzdichten Ventile ein leckagefreies Absperren des an das Ventil angeschlossenen hydraulischen Verbrauchers.The above-described known pressure control function for a commercial proportional pressure control valve is now modeled according to the invention with two seat-tight 2/2-way switching valves. The pertinent allow seat-tight valves ensure leak-free shut-off of the hydraulic consumer connected to the valve.
Um dies näher zu erläutern, wird auf die Darstellung nach der
Neben einer Spannungsversorgung
Die angesprochenen beiden Schaltventile
Der in der
Die PWM(Pulsweitenmodulierte)-Frequenz sollte vorzugsweise deutlich über der sog. Eckfrequenz der beiden Ventile
Zur weiteren Erläuterung sei auf die
Das digitale Druckregelventil nach der
Um den Druck zu ändern, wird das Schließelement der Steuerkante nach der Druckänderungsgeschwindigkeit
Da die innerhalb der erfindungsgemäßen Druckregelvorrichtung eingesetzten Schaltventile
Bei den bekannten Proportionalventilen kann der Druck nur direkt am jeweiligen Ventil geregelt werden, wohingegen bei der vorgeschlagenen erfindungsgemäßen Lösung der Drucksensor der Sensoreinrichtung
ZITATE ENTHALTEN IN DER BESCHREIBUNG QUOTES INCLUDE IN THE DESCRIPTION
Diese Liste der vom Anmelder aufgeführten Dokumente wurde automatisiert erzeugt und ist ausschließlich zur besseren Information des Lesers aufgenommen. Die Liste ist nicht Bestandteil der deutschen Patent- bzw. Gebrauchsmusteranmeldung. Das DPMA übernimmt keinerlei Haftung für etwaige Fehler oder Auslassungen.This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.
Zitierte PatentliteraturCited patent literature
- EP 2431640 A2 [0004] EP 2431640 A2 [0004]
Claims (11)
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102015007424.5A DE102015007424A1 (en) | 2015-06-09 | 2015-06-09 | Pressure control device |
EP16727304.4A EP3308236B1 (en) | 2015-06-09 | 2016-06-02 | Pressure control device |
PCT/EP2016/000897 WO2016198149A1 (en) | 2015-06-09 | 2016-06-02 | Pressure control device |
JP2017563920A JP6813507B2 (en) | 2015-06-09 | 2016-06-02 | Pressure controller |
US15/579,651 US11442478B2 (en) | 2015-06-09 | 2016-06-02 | Pressure control device |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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DE102015007424.5A DE102015007424A1 (en) | 2015-06-09 | 2015-06-09 | Pressure control device |
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US (1) | US11442478B2 (en) |
EP (1) | EP3308236B1 (en) |
JP (1) | JP6813507B2 (en) |
DE (1) | DE102015007424A1 (en) |
WO (1) | WO2016198149A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102018130820A1 (en) * | 2018-12-04 | 2020-06-04 | Schaeffler Technologies AG & Co. KG | Supply system and method for operating a supply system |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11609586B2 (en) * | 2019-10-13 | 2023-03-21 | Aaron Dwayne Lawson | Apparatuses for facilitating relieving pressure in a fluid transportation system |
DE102021108081B4 (en) | 2021-03-30 | 2023-02-02 | Andreas Lupold Hydrotechnik Gmbh | Device for controlling a hydraulic pump or a hydraulic motor |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102009057359A1 (en) * | 2008-12-08 | 2010-06-10 | CKD Corporation, Komaki-shi | Pressure control device and flow rate control device |
EP2431640A2 (en) | 2010-09-15 | 2012-03-21 | Robert Bosch GmbH | Method for controlling a ballistic movement of a retaining element of a valve |
DE102013016759A1 (en) * | 2013-10-10 | 2015-04-16 | Wabco Gmbh | Arrangement for controlling a transmission brake cylinder |
Family Cites Families (44)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1222153B (en) * | 1961-08-09 | 1966-08-04 | Hartmann & Braun Ag | Three-point controller working as a step controller |
US4244396A (en) * | 1971-08-09 | 1981-01-13 | Powell Industries, Inc. | Digital fluid flow control system |
US3858598A (en) * | 1971-12-09 | 1975-01-07 | Cameron Iron Works Inc | Pressure control apparatus |
US4117967A (en) * | 1977-05-26 | 1978-10-03 | The United States Of America As Represented By The Secretary Of The Navy | Solder extractor apparatus |
DE2811345C2 (en) * | 1978-03-16 | 1986-12-11 | Knorr-Bremse AG, 8000 München | Pressure regulators for pneumatic pressures, in particular in vehicles |
US4241750A (en) * | 1978-11-27 | 1980-12-30 | Kabushiki Kaisha Cosmo Keiki | Pressure setting device |
US4394871A (en) * | 1980-12-31 | 1983-07-26 | The Boeing Company | Programmable pressure regulator for titanium superplastic forming apparatus |
JPS61116107A (en) * | 1984-11-09 | 1986-06-03 | Hitachi Ltd | Actuator controller |
US4638837A (en) * | 1984-11-13 | 1987-01-27 | Allied Corporation | Electro/pneumatic proportional valve |
DE3502276A1 (en) * | 1985-01-24 | 1986-07-24 | Wabco Westinghouse Fahrzeugbremsen GmbH, 3000 Hannover | DEVICE FOR CONTINUOUSLY CONTROLLING A SOLENOID VALVE DESIGNED NORMALLY FOR DISCONTINUOUS OPERATION |
US4835970A (en) | 1985-08-13 | 1989-06-06 | Nissan Motor Co. Ltd. | Pneumatic power brake system |
US4904027A (en) * | 1988-10-03 | 1990-02-27 | American Standard Inc. | Digital air brake control system |
US5020564A (en) * | 1989-06-29 | 1991-06-04 | Allied-Signal Inc. | Doser system for regulating pressure in a control chamber of a test stand |
US4961441A (en) * | 1989-11-13 | 1990-10-09 | Salter Stuart C | Method and system for controlling a pressure regulator |
DE4133892C1 (en) * | 1991-10-12 | 1992-12-24 | Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De | |
US5269341A (en) * | 1993-04-13 | 1993-12-14 | Halliburton Company | Controlled high pressure relief for small volumes |
JPH0685449U (en) * | 1993-05-24 | 1994-12-06 | 株式会社小松製作所 | Exhaust plate control device |
JPH0736551A (en) * | 1993-07-20 | 1995-02-07 | Smc Corp | Pressure controller for electro-pneumatic regulator |
DE4331930A1 (en) | 1993-09-14 | 1995-03-16 | Mannesmann Ag | Pressure regulating device for pneumatic or hydraulic media |
US5499647A (en) * | 1995-01-12 | 1996-03-19 | Mac Valves, Inc. | Method and valve assembly for controlling a pilot signal |
JPH10306801A (en) * | 1997-05-01 | 1998-11-17 | Smc Corp | Control method of automatic control pneumatic apparatus |
US5813226A (en) * | 1997-09-15 | 1998-09-29 | Caterpillar Inc. | Control scheme for pressure relief |
US5954089A (en) * | 1998-04-17 | 1999-09-21 | Trw Inc. | Electromagnetic regulator utilizing alternate valve operating modes for gas pressure regulation |
US6356811B1 (en) * | 1998-10-13 | 2002-03-12 | Honeywell Measurex Devron Inc. | Control system for pneumatic actuators |
ATE281829T1 (en) * | 1999-07-13 | 2004-11-15 | Degussa | METHOD FOR PRODUCING POWDERED PARTICLE-REDUCED FORMULATIONS USING COMPRESSED GASES |
JP2001060114A (en) * | 1999-08-24 | 2001-03-06 | Smc Corp | Pressure controller |
US6216456B1 (en) * | 1999-11-15 | 2001-04-17 | Caterpillar Inc. | Load sensing hydraulic control system for variable displacement pump |
DE10033909B4 (en) * | 2000-07-12 | 2009-11-19 | Robert Bosch Gmbh | Method and device for controlling at least one valve |
US6568416B2 (en) * | 2001-02-28 | 2003-05-27 | Brian L. Andersen | Fluid flow control system, fluid delivery and control system for a fluid delivery line, and method for controlling pressure oscillations within fluid of a fluid delivery line |
EP1413047A4 (en) * | 2001-05-30 | 2009-01-21 | Nat Seating Company Inc | Truck seat height positioning system |
US7505818B1 (en) * | 2001-09-07 | 2009-03-17 | Siemens Energy & Automation, Inc. | Converter method, system and apparatus |
DE10210877A1 (en) * | 2002-03-12 | 2003-11-27 | Wabco Gmbh & Co Ohg | Valve device for actuating cylinders |
US6944524B2 (en) * | 2003-01-31 | 2005-09-13 | Marsh Bellofram Corporation | Air cylinder controller |
US7055546B2 (en) * | 2003-09-24 | 2006-06-06 | Mclaughlin John E | Fluid intake pressure regulating system |
US7578481B2 (en) * | 2005-02-25 | 2009-08-25 | The Boeing Company | Digital programmable driver for solenoid valves and associated method |
JP4765859B2 (en) * | 2006-09-15 | 2011-09-07 | 株式会社アドヴィックス | Abnormality diagnosis device for vehicle braking device and abnormality diagnosis method for vehicle braking device |
US8118256B2 (en) * | 2008-10-10 | 2012-02-21 | Goodrich Corporation | Brake shutoff valve test |
US8125754B2 (en) * | 2009-06-09 | 2012-02-28 | Vladimir Shvartsman | Micro-power pulse controller for magnetic latch solenoids, relays and valves |
JP5381514B2 (en) * | 2009-08-31 | 2014-01-08 | 株式会社アドヴィックス | Brake hydraulic pressure control device |
US9045120B2 (en) | 2011-11-04 | 2015-06-02 | Robert Bosch Gmbh | Pedal oscillation suppression |
DE102011118651A1 (en) | 2011-11-16 | 2013-05-16 | Robert Bosch Gmbh | Hydraulic drive system has monitoring unit that receives control signal and pressure signal from control unit and pressure sensor to produce error signal based on comparison signals for displaying error of switching valve |
DE102013205961A1 (en) | 2013-04-04 | 2014-10-09 | Valmet Technologies, Inc. | Safety system for a hydraulic circuit |
US20140358304A1 (en) * | 2013-06-03 | 2014-12-04 | Tescom Corporation | Method and Apparatus for Managing Fluid Supply in a Process Control System |
US9618944B2 (en) * | 2015-04-14 | 2017-04-11 | General Electric Company | Pressure controller system valve characterization |
-
2015
- 2015-06-09 DE DE102015007424.5A patent/DE102015007424A1/en not_active Withdrawn
-
2016
- 2016-06-02 JP JP2017563920A patent/JP6813507B2/en active Active
- 2016-06-02 US US15/579,651 patent/US11442478B2/en active Active
- 2016-06-02 EP EP16727304.4A patent/EP3308236B1/en active Active
- 2016-06-02 WO PCT/EP2016/000897 patent/WO2016198149A1/en active Application Filing
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102009057359A1 (en) * | 2008-12-08 | 2010-06-10 | CKD Corporation, Komaki-shi | Pressure control device and flow rate control device |
EP2431640A2 (en) | 2010-09-15 | 2012-03-21 | Robert Bosch GmbH | Method for controlling a ballistic movement of a retaining element of a valve |
DE102013016759A1 (en) * | 2013-10-10 | 2015-04-16 | Wabco Gmbh | Arrangement for controlling a transmission brake cylinder |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102018130820A1 (en) * | 2018-12-04 | 2020-06-04 | Schaeffler Technologies AG & Co. KG | Supply system and method for operating a supply system |
Also Published As
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JP2018518767A (en) | 2018-07-12 |
US20180173253A1 (en) | 2018-06-21 |
EP3308236B1 (en) | 2020-03-25 |
WO2016198149A1 (en) | 2016-12-15 |
US11442478B2 (en) | 2022-09-13 |
EP3308236A1 (en) | 2018-04-18 |
JP6813507B2 (en) | 2021-01-13 |
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